US4510847A - Apparatus for adjusting the position of an adjustable element - Google Patents

Apparatus for adjusting the position of an adjustable element Download PDF

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Publication number
US4510847A
US4510847A US06/347,071 US34707182A US4510847A US 4510847 A US4510847 A US 4510847A US 34707182 A US34707182 A US 34707182A US 4510847 A US4510847 A US 4510847A
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United States
Prior art keywords
throttles
control
adjustable
pressure
control device
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Expired - Fee Related
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US06/347,071
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English (en)
Inventor
Norbert Mucheyer
Wolfgang Kauss
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Bosch Rexroth AG
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Mannesmann Rexroth AG
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Assigned to MANNESMANN REXROTH GMBH reassignment MANNESMANN REXROTH GMBH ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KAUSS, WOLFGANG, MUCHEYER, NORBERT
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor

Definitions

  • This invention relates to an apparatus for controlling the position of a movable member and particularly for controlling a hoisting unit associated with a tractor, combine or the like.
  • This invention is an improvement on the subject matter of U.S. patent application Ser. No. 188,453, filed Sept. 18, 1980, the content of which is hereby incorporated by reference.
  • the present invention relates to the apparatus as disclosed in application Ser. No. 188,453 wherein both control devices of a multi-way valve can be controlled as desired. Because the two control devices of the main multi-way valve can be acted upon as desired, it is possible to adjust one control device to correspond to the position of the element to be adjusted, and to adjust the other control device to correspond to the force being applied to the element to be adjusted.
  • the responsiveness of a pressure ratio valve can be adjusted.
  • the responsiveness or sensitivity is high, the effect of one of the control parameters is eliminated.
  • there is strong damping or buffering of the pressure ratio valve a change in the cross section of one of the throttles designed for the nominal pressure will be fully reflected back to the control circuit.
  • bypass throttles are opened, the damping of each control device is affected by the cross section of the corresponding bypass throttle. In fact, the damping can be so pronounced that the control device becomes practically ineffective.
  • the bypass throttles are provided preferably where the exertion of predetermined force by the adjustment element effects the control device of the multi-way valve.
  • the apparatus can accomplish rapid operation of the adjustable element wherein the influx of the pressure agent from the pressure source connected with the control circuit can be switched off in order to minimize loss of power.
  • FIG. 1 is a schematic fluid and control circuit diagram of a first embodiment of an apparatus in accordance with the invention
  • FIGS. 2 and 3 are volume-pressure and throttle surfaces-pressure diagrams illustrating operational aspects of the apparatus in accordance with the invention
  • FIG. 4 illustrates a modification of the apparatus of FIG. 1
  • FIG. 5 is a circuit diagram of a further embodiment in accordance with the invention.
  • an adjustable element 1 is illustrated in the form of a simply constructed piston and cylinder apparatus which is connected by a fluid line 2 with a multi-way valve 3 which can be reciprocatingly actuated by control pressure.
  • the pressure side of a pump 5 is connected to valve 3 by a fluid line 4, the intake line 6 of pump 5 extending into a tank 7.
  • Valve 3 is connected through a line 8 with tank 7.
  • Line 4 is also connected to a pressure limiting or pressure relief valve 9 of which the discharge side is connected to tank 7.
  • Components 1 through 9 form an operating loop which is generally indicated at 10.
  • Valve 3 is provided with control devices 11 and 12 at opposite ends thereof for operating its movable slide. These devices, under the influence of a pressure medium (liquid or gas) tend to move the slide in opposition to the effects of one of the control springs 13 or 14 in the direction of arrows 15, 15a which are shown in the control devices to which they relate. The two control springs 13, 14 tend to hold the slide in its middle position, as illustrated, when control devices 11, 12 are not actuated.
  • a control line 16 is connected to control device 11 and a control line 17 is connected to control device 12.
  • a control line 18 is connected to the pressure side of a control pump 19 of which the intake line 20 is connected with tank 7.
  • a pressure limiting valve 18a is connected with control line 18.
  • a control line 21 is connected to control line 18 through a two port, two position valve 37 which leads to an adjustment throttle 22.
  • a control line 23 connects adjustment throttle 22 to an adjustment throttle 24 which is connected through a line 25 with tank 7.
  • the control line 23 is connected to control line 17.
  • Two adjustment throttles 27 and 28 are connected with control line 16 through control line 26 and the other side of adjustment throttle 27 is connected to tank 7.
  • the other side of adjustment throttle 28 is connected to control line 21.
  • Adjustment throttles 22 and 28 have mechanically movable adjustment elements which are connected with each other by a mechanical link 43 so as to be counter-rotating. These throttles are configured as a supplier of a reference setting, and adjustment throttles 24 and 27 are configured such that control parameters are applied to them, making them an actual value transmitter, connected with the movable part of adjustable element 1.
  • control device 11 In order to stabilize the control slide of valve 3 in its movement, control device 11 preferably has the same effective cross section as control device 12.
  • the volume V propelled by pump 5 through multi-way valve 3 per unit time is a function of the differential pressure, indicated as dp, applied to and influencing control devices 11, 12.
  • dp differential pressure
  • dp min minimum effective differential pressure
  • FIG. 3 shows the relationship between the cross sectional surface S of a throttle as a function of the pressure px prevailing at the input side (upstream) of the throttle under constant propulsion pressure p max produced by the control pump 19 and throttle mounted upstream of this throttle.
  • the adjustable cross section of adjustment throttles 22 to 24 is selected as follows. The essentially linear portion in the middle of the curve illustrated in FIG. 3 shows how much the cross sectional surface dS of the throttle must be reduced in order to produce the pressure deviation dp min between control devices 11, 12 in a positive or negative sense.
  • the precision with which the slide of multi-way valve 3 must respond to a variation in the cross section of one or both of adjustment throttles 22, 24 depends upon a precision G expressed in percentage.
  • the product of this and a precision factor F by which dS must be multiplied in order to attain the largest flow-through cross section of the valve necessary for control is 100.
  • the precision G is to be 2%
  • the precision factor F is equal to 50.
  • the maximum adjustable cross sectional surface of throttle 22 is the sum of the largest flow-through cross section (F ⁇ dS) necessary for the control and of the minimum flow-through cross section which is characteristic for each respective adjustment throttle.
  • the flow-through volume V is practically proportional to the level setting (for each adjusted state) wherein the same pressure is always set in line 23.
  • Bypass throttles 39 and 40 are connected in parallel with throttles 27 and 28, respectively.
  • the movable adjustment elements for throttles 39 and 40 are connected to each other by a mechanical link 41 such that the two throttles 39, 40 can only be operated together and only in the same direction.
  • the influence of throttles 27 and 28 becomes gradually smaller with progressive opening of throttles 39, 40.
  • control pump 19 and control circuit 29 can be switched on or off at will by means of the switch valve 37 which is mounted between control lines 18 and 21.
  • a second switch valve 38 has three port connections which are connected to the lines 16, 17 and 21, respectively. When the control element of switch valve 38 is in the position shown in the drawing, lines 16, 17 and 21 are disconnected from each other at the switch valve 38. In both of the other control positions of the control element of switch valve 38, line 21 is connected directly either with line 16 or with line 17.
  • the second switch valve 38 serves as a quick make or break switch for rapid operation of adjustment element 1.
  • either one of the control devices 11, 12 can be switched to pressure control whereupon pressure is fed very rapidly to element 1 which is then operated very rapidly.
  • the flow of pressure agent to control circuit 29 is cut off by closure of switch valve 37 when adjustment element 1 is sufficiently activated, i.e., when the piston within the cylinder that controls it is in its end position.
  • switch valve 37 can manually be returned to the position shown in the drawing.
  • bypass throttles 39, 40 can be entirely closed or can be opened together to a predetermined flow-through cross section. These throttles dampen the effect of control valves 27 and 28 acting on control device 11, and can completely eliminate that effect when they are totally opened. Other intermediate settings can also be attained by means of bypass valves 39, 40.
  • FIG. 4 shows an arrangement which is usable if there are no bypass throttles 39, 40 wherein throttle 28 can be configured as a pressure ratio valve 28a which holds the pressure in control device 11 at any given pressure, for example, one half of the control pressure, regardless of the size of the opening of throttle 27.
  • the sensitivity of pressure ratio valve 28a can be made adjustable by inserting an adjustable throttle 44 in its control line. If the sensitivity is high, the effect of the actual level indicator on the control device is eliminated. If the sensitivity is low, a variation in the cross section of throttle 27 can exert its full effect on control circuit 29.
  • the effectiveness of adjustment element 1 can be determined with modification of the sensitivity of pressure ratio valve 28a.
  • FIG. 5 A further embodiment of an apparatus in accordance with the invention is illustrated in FIG. 5 wherein bypass throttles 39, 40 are replaced by a pressure ratio valve 45 which is in the configuration of a three-position, three-port, proportional valve with two control devices 47 and 48.
  • Control device 47 has a smaller pressure surface than that of control device 48, and the pressure surface of control device 47 is preferably half as large as the pressure surface of control device 48.
  • Control device 47 is connected to control line 21 which also leads to a connection point of pressure ratio valve 45.
  • the second control device 48 is connected to a second connection point of pressure ratio valve 45 and also through an adjustable throttle point 46 to control line 16.
  • a third connection point of the pressure ratio valve is connected through a line 49 to tank 7.
  • pressure ratio valve 45 acts on control device 11 of multi-way valve 3 without activating throttles 27, 28. Any change in the adjustment of throttles 27 and 28 is compensated by pressure ratio valve 45. Th stronger the influence of the adjustable throttle setting 46, the lower the effect of pressure ratio valve 45 on control device 11.
  • the adjustment level can also be designated as the actual value and the reference level as the desired value.
  • adjustment throttles 22, 24 affect the position of the hoist gear train of a tractor, while adjustment throttles 27 and 28 affect its traction force.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
US06/347,071 1981-02-19 1982-02-08 Apparatus for adjusting the position of an adjustable element Expired - Fee Related US4510847A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3106086 1981-02-19
DE19813106086 DE3106086A1 (de) 1981-02-19 1981-02-19 "vorrichtung zum regeln eines stellgliedes, insbesondere zum regeln des hubwerkes eines schleppers, maehdreschers o.dgl."

Publications (1)

Publication Number Publication Date
US4510847A true US4510847A (en) 1985-04-16

Family

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Family Applications (1)

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US06/347,071 Expired - Fee Related US4510847A (en) 1981-02-19 1982-02-08 Apparatus for adjusting the position of an adjustable element

Country Status (5)

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US (1) US4510847A (fr)
DE (1) DE3106086A1 (fr)
FR (1) FR2508116B2 (fr)
GB (1) GB2094030B (fr)
IT (1) IT1154447B (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4574687A (en) * 1982-07-20 1986-03-11 Mannesmann Rexroth Gmbh Apparatus for positioning an adjusting member
US4622883A (en) * 1985-02-02 1986-11-18 Mannesmann-Rexroth Gmbh Apparatus for positioning a movable member
US4632016A (en) * 1984-03-02 1986-12-30 Mannesmann Rexroth Gmbh Apparatus for controlling an adjustable arm
US4677899A (en) * 1979-10-05 1987-07-07 Mannesmann Rexroth Gmbh Apparatus for controlling an adjustable member
US4933617A (en) * 1987-08-12 1990-06-12 Hoerbiger Hydraulik Gmbh Servo steering system for motor boats
US5079988A (en) * 1989-12-26 1992-01-14 Raymond Robert E Hydraulic sensor and transducing apparatus
US5193342A (en) * 1992-02-14 1993-03-16 Applied Power Inc. Proportional speed control of fluid power devices
US5490442A (en) * 1992-09-17 1996-02-13 Mannesmann Rexroth Gmbh Safety circuit for a servo-hydraulic regulating system

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3227060A1 (de) * 1981-02-19 1984-01-26 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum regeln eines stellgliedes, insbesondere zum regeln des hubwerkes eines schleppers, maehdreschers oder dgl.
DE3239952A1 (de) * 1982-10-28 1984-05-03 Robert Bosch Gmbh, 7000 Stuttgart Hydraulische einrichtung zur hubwerksregelung
DE3337317A1 (de) * 1983-10-13 1985-04-25 Mannesmann Rexroth GmbH, 8770 Lohr Verfahren und einrichtung zum regeln der arbeitstiefe eines von einer zugmaschine getragenen bodenbearbeitungsgeraets
DE3340676A1 (de) * 1983-11-10 1985-05-23 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum versorgen einer steueranordnung mit steuerdruckmittel
DE3524759A1 (de) * 1985-07-11 1987-01-22 Bosch Gmbh Robert Wegeventil
DE4312644C2 (de) * 1993-04-19 1996-01-25 Rexroth Mannesmann Gmbh Steuerung für einen hydraulischen Verbraucher
DE4406669C2 (de) * 1994-03-01 1997-01-30 Rexroth Mannesmann Gmbh Servohydraulisches Regelsystem
DE19744696A1 (de) * 1997-10-10 1999-04-15 Zahnradfabrik Friedrichshafen Druckregelventil
WO1998048332A1 (fr) 1997-04-18 1998-10-29 Zf Friedrichshafen Ag Soupape de reglage de pression

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3213886A (en) * 1962-10-22 1965-10-26 Pearne And Lacy Machine Compan Flow control valve with stop means movable at a controlled rate
US3583422A (en) * 1967-10-19 1971-06-08 Zahnradfabrik Friedrichshafen Valve construction for controlled pressure buildup in fluid-operated brake or clutch
US3771802A (en) * 1970-12-05 1973-11-13 Toyo Bearing Mfg Co Apparatus for controlling chucking pressures on workpieces in machine tools
US3805674A (en) * 1971-11-24 1974-04-23 Westinghouse Bremsen Apparate Hydraulic pressure control valve
US3872773A (en) * 1972-08-09 1975-03-25 Nutron Corp Position controlling
US4148248A (en) * 1975-03-11 1979-04-10 Maxton Manufacturing Company Hydraulic valve control system
US4350209A (en) * 1979-08-06 1982-09-21 Allis-Chalmers Corporation Hydraulic draft control valve
US4404897A (en) * 1974-07-18 1983-09-20 Leonard Willie B Fluidic repeater
US4421012A (en) * 1980-02-15 1983-12-20 G. L. Rexroth Gmbh Control circuit throttling valve

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2731164C2 (de) * 1977-07-09 1983-12-08 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur Hubwerksregelung bei Schleppern und Mähdreschern
DE2811585C2 (de) * 1978-03-17 1987-11-12 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulische Anstellvorrichtung mit Rückführungseinrichtung
DE2940403A1 (de) * 1979-10-05 1981-04-09 G.L. Rexroth Gmbh, 8770 Lohr Vorrichtung zur regelung eines stellgliedes, insbesondere zur regelung des hubwerkes eines schleppers, maehdreschers o.dgl.

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3213886A (en) * 1962-10-22 1965-10-26 Pearne And Lacy Machine Compan Flow control valve with stop means movable at a controlled rate
US3583422A (en) * 1967-10-19 1971-06-08 Zahnradfabrik Friedrichshafen Valve construction for controlled pressure buildup in fluid-operated brake or clutch
US3771802A (en) * 1970-12-05 1973-11-13 Toyo Bearing Mfg Co Apparatus for controlling chucking pressures on workpieces in machine tools
US3805674A (en) * 1971-11-24 1974-04-23 Westinghouse Bremsen Apparate Hydraulic pressure control valve
US3872773A (en) * 1972-08-09 1975-03-25 Nutron Corp Position controlling
US4404897A (en) * 1974-07-18 1983-09-20 Leonard Willie B Fluidic repeater
US4148248A (en) * 1975-03-11 1979-04-10 Maxton Manufacturing Company Hydraulic valve control system
US4350209A (en) * 1979-08-06 1982-09-21 Allis-Chalmers Corporation Hydraulic draft control valve
US4421012A (en) * 1980-02-15 1983-12-20 G. L. Rexroth Gmbh Control circuit throttling valve

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4677899A (en) * 1979-10-05 1987-07-07 Mannesmann Rexroth Gmbh Apparatus for controlling an adjustable member
US4574687A (en) * 1982-07-20 1986-03-11 Mannesmann Rexroth Gmbh Apparatus for positioning an adjusting member
US4632016A (en) * 1984-03-02 1986-12-30 Mannesmann Rexroth Gmbh Apparatus for controlling an adjustable arm
US4622883A (en) * 1985-02-02 1986-11-18 Mannesmann-Rexroth Gmbh Apparatus for positioning a movable member
US4933617A (en) * 1987-08-12 1990-06-12 Hoerbiger Hydraulik Gmbh Servo steering system for motor boats
US5079988A (en) * 1989-12-26 1992-01-14 Raymond Robert E Hydraulic sensor and transducing apparatus
US5193342A (en) * 1992-02-14 1993-03-16 Applied Power Inc. Proportional speed control of fluid power devices
US5319933A (en) * 1992-02-14 1994-06-14 Applied Power Inc. Proportional speed control of fluid power devices
US5490442A (en) * 1992-09-17 1996-02-13 Mannesmann Rexroth Gmbh Safety circuit for a servo-hydraulic regulating system

Also Published As

Publication number Publication date
DE3106086A1 (de) 1982-09-09
FR2508116B2 (fr) 1985-12-27
FR2508116A2 (fr) 1982-12-24
DE3106086C2 (fr) 1989-10-19
GB2094030A (en) 1982-09-08
IT8267085A0 (it) 1982-01-28
GB2094030B (en) 1985-06-05
IT1154447B (it) 1987-01-21

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